Hydraulic speed governor



Feb. 3, 1931. L. R. HUFF 1,791,028

HYDRAULIC SPEED GOVERNOR Filed Sept. 18, 1928 IN! 'EX TOR.

Leqli 0R Patented Feb. 3, 1931 NITED' STATES PATENT OFFICE LESLIE R. HUFF, O1 PHILLIPBBUBG, NEW JERSEY, ASSIGNOR '1O INGERSOLL-BAND COMPANY, OF JERSEY CITY, NEW JERSEY, A CORPORATION 01 NEW JERSEY manure sraan eovaanoa Application fled leptember 18, 1828. Serial Io. 306,715.

This invention relates to speed governors, but more particularly to a hydraulic speed governor adapted to be interposed between a source of liquid pressure, as for instance,

oil under pressure, and an element intended to be governed.

Une object of the invention is to assure a minimum amount of variance in the speed of the element intended to be governed. Another object is to render the device delicately responsive to any variation in the operating speed of a prime mover.

Other objects Wlll be in part obvious and in part pointed out hereinafter, and to all of these ends the invention consists of the combination of elements and arran ement of parts having the general mode 0 operation substantiall as hereinafter described and claimed in t e specification and illustrated in the accompanying drawing, the ligure of which illustrates a sectional elevation of the hydraulic speed governor applied to the end of a rotary member, such as the main shaft-0f a turbo blower and the like.

Referring more particularly to the drawing, A represents the casing of the machine intended to be driven, such as a turbo blower, and B a bearing of the machine in which is journalled a main shaft C. The main shaft 0 in this instance has a reduced threaded end D on which is mounted a flan e E having a recess F in which may be isposed a nut G whereby the flange E may be securely fastened to the end D of the shaft.

The flange E in the resent instance has a cylindrical projection at its forward face to extend into a recess J of a casing K for centralizing said casing with respect to the shaft 0. The casing may be secured to the flange E in any suitable manner, in the present instance-bolts L are indicated for this purpose Preferably the casing K carries an integral projection or shaft 0 which is journalled 1 n a cover plate P adjacent the casing K and 1s secured to the end of the frame A by means of bolts Q. The cover plate P may be provided with an integral extension R which supports at its outer end a plate S to act as a beari shaft O In the construction shown the shaft 0 serves as a mounting for an impeller T adapted to draw li uid, such as oil from a reservoir slnotshown throughapi e Such oil is disc arged from the impel er T into a discharge chamber V formed in this instance in the cover plate P. The function of the pump comprisingthe impeller T and the discharge chamber V is to supply oil to the various bearin s of the machine to which the device may 0' attached. The pump is accordingly provided with a pipe W through which the oil may fiow from the pump chambelardV to the bearings intended to be supp 1e The pump mechanism illustrated is merely shown as one means of supplyin lubricant under pressure to the machine. ft is therefore to be understood that the invention is in no wise limited in its applicabilit to any particular type of machine intende to be lubricated or to any specific type of pumping mechanism.

The casing K is provided with a valve chamber X which extends transversely through the casing K and preferably through the axis of rotation ofthe shaft C. A plug Y forms a closure for one end of the valve chamber X and a stop plug Z is threaded into the opposite end of the valve chamber and has a pro'ection 6 extending into the valve chamber K,

Formed in the shaft 0 is an inlet passa c which communicates at one end with t e valve chamber X and atits other end with a pipe d leading from the ipe W. At the end of the inlet passage 0 ad iacent the pipe d is an annular roove e to assure constant communication etween the inlet passage 0 and the source of oil suppl A connecting passage f also formed in t e shaft 0 leads from the valve chamber X to an annular groove 9 in the shaft 0 which is in constant communication with a pipe 71, communicating with the groove 9 through a passage 7'. The casing K in this instance also has an exhaust port 70 adjacent the connecting passage f.

for the outer or free end of the Disposed within the valve chamber X is a i valve 0 of the lug type having an external groove p of suc proportions as to afford communication between either the inlet passage 0 and the connecting passage f or between the connecting passage f and the exhaust port k, depending upon t e position of the valve. A transverse passa e q in the valve 0 conveys oil from the annu ar groove p to a longitudinal passage 1' in the valve and through which such oil may pass to the internal face of the plug Y forming a column along the passage 1 to act against the end of the valve 0 and thus resist movement of the valve.

The valve 0 in this instance is off-set with respect to the axis of rotation of the shaft C so that its center of gravity will lie to one side of the longitudinal axis of the shaft. This position of the valve will at all times be assured since the projection b of the plug Z serves to limit movement of the valve in a direction in which the center of gravity of the valve might otherwise move into coincidence with the longitudinal axis of the shaft. In the drawing a practical use of the device is shown. The pipe h into which the 011 from the connecting passage f passes is shown connected at its opposite end to a relay valve 8. The relay valve 8 comprises a cylinder t and a piston u disposed in the cylinder t, the pipe h being connected to the cylinder t in such a manner that oil will only be introduced into the cylinder beneath the piston u. The pistonu is normally held in the retracted position by a sprin 'v seated on the piston at one end and with its other end on a sprin seat to which bears against the end of an ad usting screw :0, said ad usting screw a: having a hand wheel 3 whereby the tension of the spring '0 may be varied to suit immediate requirements.

Connected to the piston u is a rod 2 which extends slidably through the spring seat on and the adjusting screw a: and is pivotally connected at its outer or free end to a floating lever 2. The opposite end of the floating lever may be pivotally connected to a rod 3 connected to a steam admission valve 4 in a valve casing 5 through which motive fluid, such as steam, may flow from a source of supply to a prime mover (not shown), but which may be a steam engine whereby the turbo blower is actuated. The base 6 of a bracket 7 forms a cover for the top of the valve casing 5 and supports at its top a cylinder 8 in which is disposed a spring pressed iston 9 threaded in this instance to the en of the rod 8.

Suitable means are provided for controlling the admission ofpower, such as 011 under pressure, to the ends of the cylinder 8 for actuating the piston 9 and consequently the valve 4. To this end a chamber 10 is formed in a valve chest 11 preferably adjacent the cylinder 8 to receive slidably a pilot valve 12 having end heads 13 and 1.4 and an interhead 13 in mediate head or flange 15. The

16 leading this instance controls a passa to the u per end of the cylin er 8 and the interme iate flange 15 controls a passage 17 leading to the lowermost end of the cylinder 8. The head 14 acts merel as a guide for the valve and also forms a closure for one end of the valve chamber 10. Oil for actuating the pilot valve 12 is admitted into a chamber 18 in the valve chest 11 through a passa e 19 and from thence passes into the valve c amber 10 through ports 20 formed in this instance in a valve bushing 21 inserted in the valve chest 11.

Inasmuch that the elements intended to be actuated, such as the relay valve 8 and the 1lot valve 12 and the steam valve 4, do not orm a part of the present invention but are merely shown for the purpose of illustrating one mode of application of the invention, further description thereof is considered unnecessary, it being intended merely to illustrate elements of a type in which it is preferable or desirable to actuate said elements at oil pressures lower than the pressure of the oil supplied for lubricating purposes.

The operation of the device is as follows: Let it be assumed the shaft C and the casing K are being rotated, oil will then be drawn through the pipe U by the impeller T and discharged into the ischarge chamber V from whence it flows into the pipe W and into the pipe d. Inasmuch that the inlet passage c is in constant communication with the pipe (1 oil will also flow through the inlet passage c and through the groove p and the passages q and r to the internal face of the plug Y forming a column alon the passage 1- to act agfinst the valve 0. wing to the fact that t e center of gravity of the valve 0 lies to one side of the axis of rotation of the shaft C, said valve will be centrifugally forced in an outwardly direction towards the plug Y thus tendingeto increase the area of communication tween the groove p and the inletpassage cto wider limits. in passing from the inlet groove isalwaysconsidera ly restricted even when t e valve moves towards the plug Y and the pressure of the oil in the passages g and r as well as that in the connectin passage f will therefore be of consideraby lower value than the pressure of the oil in the inlet passa c. The oil existing in the passage f and t e pi h and under this lower value premure will then act against the piston u tending to raise said-piston against the pressure exerted thereon by the spring 0.

During the time that the prime mover is operating at thenormal rate of speed, the pressure in the connecting passage f and therefore beneath the piston u will not have the effect of raising the piston u and therefore disturbing the position of the admission valve 4. When, however, due to various .The oil however, passage 0 into the causes, the speed of the main shaft C increases, the increased speed of the shaft will cause the valve 0 to be thrown in an outwardly direction towards the plug Y, thus opening the area of communication between the inlet passage 0 and the groove 1 to wider limits. The oil in the passage 0 is then able to flow more freely through the groove p and so an increase of pressure will take place in the area of lower pressure existing in the passage f. Oil under higher pressure will then flow into the connecting passage f and through the pipe h beneath the piston u to raise said piston in the cylinder t. This move ment of the piston u will raise the pilot valve 12 so that oil may flow from the chamber 18 through the ports 20 into the valve chamber 10 and thence through the passage 16 into the cylinder 8 to act on the upper surface of the piston 9 for depressing the admission valve 4 and thus reducing the flow of steam to the prime mover. This of course will have the effect of decreasing the speed of the shaft C and as a consequence the centrifugal force acting on the valve 0 will lessen and the valve 0 will again move in the direction of the stop plug Z restricting the opening between the groove p and passage 0 and thus reducing the amount of oil entering the groove 12 from the inlet passage 0.

When the speed of the shaft C has been reduced to such an extent that the centrifugal force moving the valve 0 towards the plug Y lessens and the valve 0 moves towards the plug Y, the port It becomes uncovered and in communication with the annular groove p. The passage 0 is now covered by the movement of the valve 0 and the pressure of the oil in this passage 0 cannot act upon the oil in the passage f. The pressure upon the oil in the passage fbeing thus eliminated and the port In being uncovered it will be apparent that the oil in this pa$age 1' will flow through the port It into the sump in the main frame A. This action is expedited by the spring 1; in the cylinder t which, now that pressure upon the oil is removed, will actuate the piston u downwardly to empty the cylinder 25 of oil. This retraction of the piston u to the bottom of the cylinder t will move the ilot valve 12 downwardly so that oil may ow from the chamber 18 into the valve chamber 10' between the heads 13 and 15 and thence through the passage 17 beneath the piston 9 to raise said piston and consequently also the admission valve 4 to again admit a greater amountof steam to the prime mover.

I claim: v

1. A hydraulic speed governor, comprising a casing adapted to be attached to a rotary member, a valve chamber in the casing extending through the axis of rotation of the casing, said casing having an inlet passage opening into the valve chamber and in constant communication with a source of l quid pressure supply, a connecting passa e in the casin for conveying liquid from t e valve cham er to an element intended to be actuated, and a valve in the valve chamber adapted to be centrifugally actuated and having an external groove to afiord communication betwen the inlet and connecting passages, said valve having a passage for conveying liquid from the groove into the end of the valve chamber to act against the valve.

2. A hydraulic speed governor, comprising a casing adapted to be attached to a rotary member, a valve chamber in the casing extending through the axis of rotation of the casing, said casing having an inlet passage leading from a source of liquid pressure supply to the valve chamber, a connecting passage in the casing for conveying liquid from the valve chamber to an element intended to be supplied, a valve in the valve chamber oil'- set with respect to the axis of rotation of the casing to enable said valve to be centrifugally actuated toward the end of the valve chamber during the rotation of the casing, an external groove in the valve to afi'ord communication between the inlet and connecting passages, and a passage in the valve conveying liquid into the end of the valve chamber to act against the end of the valve.

3. A hydraulic speed governor, comprising a casing adapted to be attached to a rotary member and having a valve chamber extending through the axis of rotation of the casing, said casing having an exhaust port leading from the valve chamber to the exterior of the casing, an inlet passage and a connecting passage in the casing opening into the valve. chamber, and a valve in the valve chamber having an external groove and being ofl'set with respect to the axis of rotation of the casing to enable said valve to be centrifugally actuated for controlling communication by said groove between the inlet and connecting passages and between the connecting passage and the exhaust port to maintain a pressure in the exhaust assage.

4. A hydraulic speed governor, comprising a casing adapted to be attached to a rotary member and having a valve chamber therein. a projection on the casing having an inlet and a connecting dpassage extending into the valve the valve chamber having a groove therearound extending across the inlet and con- 7 necting passa es and adapted to be centrifugally moved y the rotation of the rotary member to chan the relationship between the oove and t e said passages, and means on t e casing extending into the chamber to limit the movement of said valve.

6. A hydraulic speed governor, comprising a casing adapted to be attached to a rotary 10 member and havin an exhaust port and a valve chamber therein, a projection on the casing having an inlet and a connecting passage extending into the valve chamber adjacent the exhaust port, and a centrifugally operated valve in the valve chamber having a roove therearound extending across the inet and connecting passages and adapted to be centrifugally moved by the rotation of the rotary member to change the relationship between the groove and the said passages, said movement in one direction causin the inlet to be covered by the valve and t e exhaust port to be uncovered b the groove.

7. A hydraulic spe'e governor, comprising :5 a casing adapted to be attached to a rotary member and having an exhaust port and a valve chamber therein, a projection on the casing having an inlet and a connecting passage extending into the valve chamber adjaao cent the exhaust port, a centrifugally operated valve in the valve chamber having a groove therearound extending across the inlet and connecting passages and adapted to be centrifu ally moved by the rotation of the as rotary mem er to change the relationship between the groove and the said passa 's, said movement in one direction causing t e inlet to be covered by the valve and the exhaust port to be uncovered by the groove, and means 40 extendin into the chamber to limit the movement of the valve in said direction.

In testimonywhereof I have signed this specification.

LESLIE R. HUFF. 

